CN104053959B - Conditioner - Google Patents

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Publication number
CN104053959B
CN104053959B CN201280067172.XA CN201280067172A CN104053959B CN 104053959 B CN104053959 B CN 104053959B CN 201280067172 A CN201280067172 A CN 201280067172A CN 104053959 B CN104053959 B CN 104053959B
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CN
China
Prior art keywords
control device
heat exchanger
cold
producing medium
conditioner
Prior art date
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Active
Application number
CN201280067172.XA
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Chinese (zh)
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CN104053959A (en
Inventor
竹中直史
若本慎一
山下浩司
森本裕之
鸠村杰
石村亮宗
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Mitsubishi Electric Corp
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Mitsubishi Electric Corp
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Publication of CN104053959A publication Critical patent/CN104053959A/en
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Publication of CN104053959B publication Critical patent/CN104053959B/en
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B1/00—Compression machines, plants or systems with non-reversible cycle
    • F25B1/10—Compression machines, plants or systems with non-reversible cycle with multi-stage compression
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B13/00—Compression machines, plants or systems, with reversible cycle
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B30/00—Heat pumps
    • F25B30/02—Heat pumps of the compression type
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
    • F25B2313/005—Outdoor unit expansion valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
    • F25B2313/006—Compression machines, plants or systems with reversible cycle not otherwise provided for two pipes connecting the outdoor side to the indoor side with multiple indoor units
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
    • F25B2313/023—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple indoor units
    • F25B2313/0233—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple indoor units in parallel arrangements
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
    • F25B2313/027—Compression machines, plants or systems with reversible cycle not otherwise provided for characterised by the reversing means
    • F25B2313/0272—Compression machines, plants or systems with reversible cycle not otherwise provided for characterised by the reversing means using bridge circuits of one-way valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
    • F25B2313/027—Compression machines, plants or systems with reversible cycle not otherwise provided for characterised by the reversing means
    • F25B2313/02741—Compression machines, plants or systems with reversible cycle not otherwise provided for characterised by the reversing means using one four-way valve
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
    • F25B2400/13—Economisers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2600/00—Control issues
    • F25B2600/25—Control of valves
    • F25B2600/2509—Economiser valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2700/00—Sensing or detecting of parameters; Sensors therefor
    • F25B2700/19—Pressures
    • F25B2700/193—Pressures of the compressor
    • F25B2700/1931—Discharge pressures
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2700/00—Sensing or detecting of parameters; Sensors therefor
    • F25B2700/21—Temperatures
    • F25B2700/2115—Temperatures of a compressor or the drive means therefor
    • F25B2700/21152—Temperatures of a compressor or the drive means therefor at the discharge side of the compressor

Landscapes

  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Compression-Type Refrigeration Machines With Reversible Cycles (AREA)
  • Air Conditioning Control Device (AREA)

Abstract

Conditioner (100) has: outside volume control device (the 4th volume control device 22), and it generates the middle pressure being used for injecting to compressor (1); Bypass flow control device (the 6th volume control device 26), itself and outside volume control device are arranged in parallel and make on the bypass pipe arrangement (25) of outdoor heat exchanger (3) bypass, the heat exchange amount of control room external heat exchanger (3) together with the volume control device of outside.

Description

Conditioner
Technical field
The present invention relates to the conditioner utilizing kind of refrigeration cycle to carry out cooling and warming, especially can carry out respectively heating or freezing and the conditioner that the utilization improvement of the compressor of cold-producing medium can be injected in compression section about achieving multiple indoor set.
Background technology
In the past, there is following conditioner, that is, 1 or multiple stage off-premises station connect multiple stage indoor set, can implement cooling operation that each indoor set only carries out freezing, only carry out heating heat running, in each indoor set, carry out the mixing running of freezing, heating respectively simultaneously.During this conditioner heating when low outer temperature, in general, the suction density of compressor reduces, and refrigerant flow, heating capacity reduce.Therefore, in the midway of the compression section of compressor, improve heating capacity by injection cold-producing medium.Such as Patent Document 1 discloses the refrigerant loop of air conditioner while of the changes in temperature with the compressor that can inject.
In addition; in recent years; protect from the view point of earth environment; as the cold-producing medium for air-conditioning, studying the switching of cold-producing medium high for the global warming coefficients (GWP) such as existing R410A cold-producing medium, R407C cold-producing medium, R134a cold-producing medium to the low cold-producing medium of the GWP such as carbon dioxide coolant, ammonia refrigerant, hydrocarbon refrigerant, tetrafluoropropane (HFO) class cold-producing medium, difluoromethane (R32) cold-producing medium.In the cold-producing medium that these GWP are low, evaporation, the condensing pressure of R32 cold-producing medium are roughly the same with R410A cold-producing medium, and the refrigerating capacity of unit mass, unit volume is larger than R410A cold-producing medium, can realize the miniaturization of equipment.
Accordingly, the mix refrigerant adopting the cold-producing medium of R32 cold-producing medium or R32 cold-producing medium and HFO cold-producing medium etc. is very by future.But R32 cold-producing medium is compared with R410A cold-producing medium, and the suction density discharge temperature that is little, compressor with compressor uprises such feature.Such as, when evaporating temperature be 5 DEG C, condensation temperature is 45 DEG C, compressor sucks time the degree of superheat of cold-producing medium be 1 DEG C, R32 cold-producing medium is compared with R410A cold-producing medium, and discharge temperature rises about 20 DEG C.Compressor is according to the guarantee temperature etc. of refrigerating machine oil, encapsulant, determine the higher limit of discharge temperature, convert R32 cold-producing medium to, when comprising the mix refrigerant of R32 cold-producing medium as composition, needs can reduce the countermeasure of discharge temperature, are effective by injecting the reduction of discharge temperature.
Prior art document
Patent document
Patent document 1: Japanese Unexamined Patent Publication 2009-198099 publication ([0044] ~ [0064], Fig. 1 etc.)
Summary of the invention
In the conditioner that patent document 1 is recorded, can carrying out in the refrigerant loop structure that changes in temperature operate simultaneously, being provided with for making it have pressure control device in function of injection (heat source machine effluent amount control device 135), injection pipe arrangement (injection-tube 161) and injected current amount control device (injected current amount control device 163).But, in the conditioner that patent document 1 is recorded, the heat exchange amount control device (thermal source pusher side first electromagnetic opening and closing valve 132, thermal source pusher side second electromagnetic opening and closing valve 133) of heat exchange amount and the middle pressure control device of adjustment outdoor heat exchanger are connected in series, and exist because their pressure loss makes the reduction of cooling and warming performance or in order to prevent the increase of the pressure loss from making the problem maximized in valve port footpath.
The present invention researches and develops to solve above-mentioned problem, its objective is and realize a kind of conditioner, even if load state changes, the heat exchange amount that also stably can carry out outdoor heat exchanger controls or injection control, keep the reliability of the compressor produced by the reduction of discharge temperature, further, can operate with the state that efficiency is high.
Conditioner of the present invention has: compressor, and it can inject the cold-producing medium of pressure by injection pipe arrangement in the compression midway of cold-producing medium; Outdoor heat exchanger; Flow passage selector device, it switches the connection of described outdoor heat exchanger; Injected current amount control device, it controls the injection flow to described compressor; Outside volume control device, it generates presses in injecting to described compressor; Bypass flow control device, itself and described outside volume control device are arranged on the bypass pipe arrangement making described outdoor heat exchanger bypass in parallel, and control the heat exchange amount of described outdoor heat exchanger together with the volume control device of described outside; Indoor heat exchanger; With indoor volume control device, its adjustment is to the refrigerant flow of described indoor heat exchanger, described compressor, described outdoor heat exchanger, described flow passage selector device, described injected current amount control device, described outside volume control device, described bypass flow control device are built in off-premises station, described indoor heat exchanger, described indoor volume control device are built in indoor set, described indoor set is connected multiple with described off-premises station in parallel.
The effect of invention
According to conditioner of the present invention, volume control device and bypass flow control device outside junction chamber in parallel, thus the discharge temperature of the cold-producing medium of discharging from compressor can be reduced, compressor with while the state running that reliability is high, can realize the running of the excellent in efficiency corresponding to the load of indoor.
Accompanying drawing explanation
Fig. 1 is the refrigerant loop figure of an example of the refrigerant loop structure of the conditioner representing embodiments of the present invention 1.
Fig. 2 represents the result of calculation of the discharge temperature of the ratio relative to R32 of the mix refrigerant of R410A, R32 and HFO1234yf, the mix refrigerant of R32 and HFO1234ze.
The P-h line chart of the migration of cold-producing medium during cooling operation when Fig. 3 is not injecting of the conditioner representing embodiments of the present invention 1.
The P-h line chart of the migration of cold-producing medium during cooling operation when Fig. 4 is the injection of the conditioner representing embodiments of the present invention 1.
When Fig. 5 is not injecting of the conditioner representing embodiments of the present invention 1 heat running time the P-h line chart of migration of cold-producing medium.
When Fig. 6 is the injection of the conditioner representing embodiments of the present invention 1 heat running time the P-h line chart of migration of cold-producing medium.
The P-h line chart of the migration of cold-producing medium when refrigeration main body when Fig. 7 is not injecting of the conditioner representing embodiments of the present invention 1 operates.
The P-h line chart of the migration of cold-producing medium when refrigeration main body when Fig. 8 is the injection of the conditioner representing embodiments of the present invention 1 operates.
The P-h line chart heating the migration of cold-producing medium when main body operates when Fig. 9 is not injecting of the conditioner representing embodiments of the present invention 1.
The P-h line chart heating the migration of cold-producing medium when main body operates when Figure 10 is the injection of the conditioner representing embodiments of the present invention 1.
Figure 11 is the refrigerant loop figure of another example of the refrigerant loop structure of the conditioner representing embodiments of the present invention 1.
Figure 12 is the flow chart of the control flow that heat exchange amount controls and injection controls of the outdoor heat exchanger performed by conditioner representing embodiments of the present invention 1.
Figure 13 is the flow chart of the detailed control flow that the heat exchange amount of the outdoor heat exchanger performed by conditioner representing embodiments of the present invention 1 controls.
Figure 14 is the flow chart representing the detailed control flow that the injection performed by conditioner of embodiments of the present invention 1 controls.
Figure 15 is the refrigerant loop figure of the another example of the refrigerant loop structure of the conditioner representing embodiments of the present invention 1.
The flow chart of control flow when Figure 16 is the control method representing the conditioner selecting embodiments of the present invention 1.
Figure 17 is the summary loop structure figure of an example of the refrigerant loop structure of the conditioner representing embodiments of the present invention 2.
Figure 18 is the summary loop structure figure of an example of the refrigerant loop structure of the conditioner representing embodiments of the present invention 3.
Figure 19 is the summary loop structure figure of another example of the refrigerant loop structure of the conditioner representing embodiments of the present invention 3.
Figure 20 is the summary loop structure figure of an example of the refrigerant loop structure of the conditioner representing embodiments of the present invention 4.
Figure 21 is the summary loop structure figure of an example of the refrigerant loop structure of the conditioner representing embodiments of the present invention 5.
Detailed description of the invention
Below, based on accompanying drawing, embodiments of the present invention are described.
Embodiment 1
Fig. 1 is the refrigerant loop figure of an example of the refrigerant loop structure of the conditioner 100 representing embodiments of the present invention 1.The loop structure of conditioner 100 is described based on Fig. 1.This conditioner, by utilizing kind of refrigeration cycle, can each indoor set of unrestricted choice be refrigeration mode or heating mode.In addition, comprise Fig. 1, in figures in the following, the magnitude relationship of each component parts is sometimes different from reality.
In FIG, conditioner 100 has off-premises station (heat source machine) A, the multiple stage indoor set C ~ E of connection parallel with one another, the repeater B between off-premises station A and indoor set C ~ E.In addition, in present embodiment 1, the situation that 1 heat source machine connects 1 repeater and 3 indoor sets is described, but each connects number of units and is not limited to illustrated number of units, also can connect the indoor set of the heat source machine of such as more than 2, the repeater of more than 2 and more than 2.
Off-premises station A and repeater B is connected by the first refrigerant piping 6 and second refrigerant pipe arrangement 7.Repeater B and indoor set C ~ E is connected respectively by first indoor pusher side refrigerant piping 6c ~ 6e of each indoor pusher side and second indoor pusher side refrigerant piping 7c ~ 7e of indoor pusher side.
First refrigerant piping 6 is the pipe arrangements of the particle size connecting four-way switching valve 2 and repeater B.First indoor pusher side refrigerant piping 6c ~ 6e of indoor pusher side connects the indoor heat exchanger 5c ~ 5e of indoor set C ~ E and repeater B and respectively from the pipe arrangement of the first refrigerant piping 6 branch.Second refrigerant pipe arrangement 7 is the pipe arrangements in footpath thinner than first refrigerant piping 6 of junction chamber external heat exchanger 3 and repeater B.Second indoor pusher side refrigerant piping 7c ~ 7e of indoor pusher side connects the indoor heat exchanger 5c ~ 5e of indoor set C ~ E and repeater B and respectively from the pipe arrangement of second refrigerant pipe arrangement 7 branch.
[off-premises station A]
Off-premises station A is configured in the space (such as roof etc.) outside the buildings such as mansion usually, and supplies cold energy or heat energy by repeater B to indoor set C ~ E.But, off-premises station A is not limited to situation disposed in the outdoor, also the besieged spaces such as the Machine Room such as with scavenge port can be arranged on, if used heat can be discharged to outside building by blast pipe, then also can be arranged on the inside of building, or also can use water-cooled off-premises station A and be arranged on the inside of building.No matter off-premises station A is arranged on any place, all special problem can not occurs.
Off-premises station A is built-in with the compressor 1 of the cold-producing medium of pressure in can being injected to the midway of high pressure by the refrigerant compression of low pressure, the flow passage selector device switching the cold-producing medium circulating direction of off-premises station A and four-way switching valve 2, outdoor heat exchanger 3 and reservoir 4.They are connected by the first refrigerant piping 6 and second refrigerant pipe arrangement 7.
In addition, near outdoor heat exchanger 3, be provided with the volume control device 3-a controlling to carry out the flow of the fluid of heat exchange with cold-producing medium.In addition, below, an example as outdoor heat exchanger 3 uses the outdoor heat exchanger 3 of air-cooled type to be described, an example as volume control device 3-a uses outdoor fan 3-a to be described, but as long as cold-producing medium and other fluids carry out the mode of heat exchange, also other modes such as water-cooled (in this situation, volume control device 3-a is pump) can be adopted.In addition, the control method of compressor 1, outdoor fan 3-a and the changing method of four-way switching valve 2 are illustrated below.
In addition, in off-premises station A, be provided with the first connecting pipings 60a, the second connecting pipings 60b, check-valves 18, check-valves 19, check-valves 20 and check-valves 21.By arranging the first connecting pipings 60a, the second connecting pipings 60b, check-valves 18, check-valves 19, check-valves 20 and check-valves 21, regardless of the closure of four-way switching valve 2, the cold-producing medium of high pressure all flows out via in second refrigerant pipe arrangement 7 outdoor machine A, and the cold-producing medium of low pressure flows in off-premises station A via the first refrigerant piping 6.
Compressor 1 sucks heat source side cold-producing medium and compresses this heat source side cold-producing medium and be in the state of HTHP, such as, by can the frequency-changeable compressor etc. of control capability form.In addition, as long as compressor 1 can inject in the form of cold-producing medium of pressure, also can be the arbitrary form of the form of such as collaborating directly to the form of the cold-producing medium of pressure in the cold-producing medium injection in the compression process be in discharge chambe or the cold-producing medium of pressing in using split-compressor or two compressors to make and the cold-producing medium between the discharge chambe of rudimentary side is discharged to the discharge chambe being inhaled into senior side in 1 compressor etc.
The flowing of cold-producing medium when four-way switching valve 2 is for switching flowing and the cooling operation of heat source side cold-producing medium when heating running.Outdoor heat exchanger (thermal source pusher side heat exchanger) 3 plays function when heating running as evaporimeter, function is played as condenser (or radiator) when cooling operation, carry out heat exchange between the air that fan 3-a supplies outdoor and heat source side cold-producing medium, make this heat source side cold-producing medium evaporate gasification or condensation liquefaction.Reservoir 4 is arranged on the suction side of compressor 1, store by when heating running and cooling operation time the residual refrigerant that produces of difference or residual refrigerant for cambic running change.
Check-valves 18 is arranged on the second refrigerant pipe arrangement 7 between outdoor heat exchanger 3 and repeater B, only in the upper flowing allowing heat source side cold-producing medium of prescribed direction (machine A is to the direction of repeater B outdoor).Check-valves 19 is arranged on the first refrigerant piping 6 between repeater B and four-way switching valve 2, only allows the flowing of heat source side cold-producing medium in prescribed direction (from repeater B to the direction of off-premises station A).Check-valves 20 is arranged on the first connecting pipings 60a, makes the heat source side cold-producing medium of discharging from compressor 1 circulate to repeater B when heating running.Check-valves 21 is arranged on the second connecting pipings 60b, makes the heat source side cold-producing medium returned from repeater B circulate to the suction side of compressor 1 when heating running.
First connecting pipings 60a in off-premises station A, for connecting the first refrigerant piping 6 between four-way switching valve 2 and check-valves 19 and the second refrigerant pipe arrangement 7 between check-valves 18 and repeater B.Second connecting pipings 60b in off-premises station A, for connecting the first refrigerant piping 6 between check-valves 19 and repeater B and the second refrigerant pipe arrangement 7 between outdoor heat exchanger 3 and check-valves 18.
In addition, in off-premises station A, pressure gauge 51, pressure gauge 52, pressure gauge 53, thermometer 54 is provided with.Pressure gauge 51 is arranged on the discharge side of compressor 1, for measuring the pressure of the cold-producing medium of discharging from compressor 1.Pressure gauge 52 is arranged on the suction side of compressor 1, for measuring the pressure of the cold-producing medium being inhaled into compressor 1.Pressure gauge 53 is arranged on the upstream side of check-valves 18, for measuring the pressure of the cold-producing medium of the upstream side of check-valves 18, middle pressure.Thermometer 54 is arranged on the discharge side of compressor 1, for measuring the temperature of the cold-producing medium of discharging from compressor 1.The information (temperature information, pressure information) detected by these checkout gears is sent to the control device (such as control device 50) of the action of Comprehensive Control conditioner 100, is used to the control of each executing agency.
And, in off-premises station A, be provided with the 4th volume control device (outside volume control device) 22, injection pipe arrangement 23, the 5th volume control device (injected current amount control device) the 24, the 3rd bypass pipe arrangement 25, the 6th volume control device (bypass flow control device) 26.
4th volume control device 22 is arranged on check-valves 21, between check-valves 18 and outdoor heat exchanger 3, freely openable.4th volume control device 22 plays the function of pressure in the cold-producing medium generating and inject to compressor 1.Injection pipe arrangement 23 is the pipe arrangements arranged for being injected to compressor 1 by the cold-producing medium of middle pressure, from check-valves 21, second refrigerant pipe arrangement 7 branch between check-valves 18 and the 4th volume control device 22 be connected to the illustrated injection port of omission of compressor 1.
5th volume control device 24 is arranged on the midway of injection pipe arrangement 23, freely openable.The refrigerant flow injected to compressor 1 is adjusted by the 5th volume control device 24.3rd bypass pipe arrangement 25 is the pipe arrangements arranged for making outdoor heat exchanger 3 bypass.6th volume control device 26 is arranged on the midway of the 3rd bypass pipe arrangement 25, freely openable.The refrigerant flow of outdoor heat exchanger 3 is flowed into by the adjustment of the 6th volume control device 26.
And, in conditioner 100, be provided with control device 50.The detailed description of this control device 50 is illustrated below, the information (refrigerant pressure information, refrigerant temperature information, outdoor temperature information and indoor temperature information) that the various detectors that control device 50 has based on conditioner 100 detect, controls the driving of the driving of compressor 1, the switching of four-way switching valve 2, the driving of the fan electromotor of outdoor fan 3-a, the aperture of volume control device (the first ~ five volume control device), the fan electromotor of indoor fan 5-m.In addition, control device 50 has the memory 50a of the function storing each controlling value of decision etc.
[repeater B]
Although repeater B is arranged on be such as the inside of building but the space such as portion in the space different from the interior space and ceiling, cold energy machine A outdoor supplied or heat energy are delivered to indoor set C ~ E.But repeater B can also be arranged on the sharing space etc. with elevator etc. in addition.
Repeater B is built-in with the first branch 10, second branch 11, gas-liquid separation device 12, first bypass pipe arrangement 14a, the second bypass pipe arrangement 14b, second amount control device 13, the 3rd volume control device 15, First Heat Exchanger 17, second heat exchanger 16 and control device 50.In addition, control device 50 has the structure same with the control device 50 of off-premises station A, function.
First branch 10 is corresponding with indoor set C ~ E, and enables first of indoor pusher side indoor pusher side refrigerant piping 6c ~ 6e be connected to the first refrigerant piping 6 or second refrigerant pipe arrangement 7 with switching.There is the magnetic valve 8c ~ 8h on first indoor pusher side refrigerant piping 6c ~ 6e of pusher side disposed in the interior in this first branch 10.First indoor pusher side refrigerant piping 6c ~ 6e of indoor pusher side is branched at the first branch 10, the side be branched is connected to the first refrigerant piping 6 via magnetic valve 8c ~ 8e, and the opposing party be branched is connected to second refrigerant pipe arrangement 7 via magnetic valve 8f ~ 8h.
Magnetic valve 8c ~ 8h, by being opened and closed control, can be connected to first indoor pusher side refrigerant piping 6c ~ 6e of indoor pusher side and the first refrigerant piping 6 or second refrigerant pipe arrangement 7 side with switching.In addition, magnetic valve 8c, 8f on first of pusher side disposed in the interior indoor pusher side refrigerant piping 6c are called the first magnetic valve, magnetic valve 8d, 8g on first refrigerant piping 6d of pusher side disposed in the interior are called the second magnetic valve, magnetic valve 8e, 8h on the first refrigerant piping 6e of pusher side disposed in the interior are called the 3rd magnetic valve.
Second branch 11 is corresponding with indoor set C ~ E, and the first bypass pipe arrangement 14a second refrigerant pipe arrangement 7c ~ 7e of indoor pusher side is connected in following repeater B and the second bypass pipe arrangement 14b.This second branch 11 has the junction portion of the first bypass pipe arrangement 14a and the second bypass pipe arrangement 14b.Gas-liquid separation device 12 is arranged on the midway of second refrigerant pipe arrangement 7, for the cold-producing medium that gas-liquid separation flows into via second refrigerant pipe arrangement 7.And, flowed to the first branch 10 by the gas phase portion that gas-liquid separation device 12 is separated, flowed to the second branch 11 by the liquid phase part that gas-liquid separation device 12 is separated.
First bypass pipe arrangement 14a is the pipe arrangement linking gas-liquid separation device 12 and the second branch 11 in repeater B.Second bypass pipe arrangement 14b is the pipe arrangement linking the second branch 11 and the first refrigerant piping 6 in repeater B.Second amount control device 13 is arranged on the midway of the first bypass pipe arrangement 14a, freely openable.3rd volume control device 15 is arranged on the midway of the second bypass pipe arrangement 14b, freely openable.
First Heat Exchanger 17 is the heat exchangers arranged to make the cold-producing medium between the 3rd volume control device 15 of the cold-producing medium between the gas-liquid separation device 12 of the first bypass pipe arrangement 14a and second amount control device 13 and the second bypass pipe arrangement 14b and the first refrigerant piping 6 carry out heat exchange.Second heat exchanger 16 is the heat exchangers arranged to make the cold-producing medium between the 3rd volume control device 15 of the cold-producing medium between the second amount control device 13 of the first bypass pipe arrangement 14a and the second branch 11 and the second bypass pipe arrangement 14b and First Heat Exchanger 17 carry out heat exchange.
In addition, also the flow channel switching valves such as check-valves can be set at the second branch 11, make the cold-producing medium flowing into the second branch 11 from the indoor set carrying out heating flow into the second heat exchanger 16.In this case, the cold-producing medium before input the 3rd volume control device 15 reliably becomes single-phase liquid refrigerant, thus can realize stable flow-control.
[indoor set C ~ E]
Indoor set C ~ E be arranged on respectively can to indoor etc. the position of air-conditioning object space supply Air Conditioning, by the cold energy from off-premises station A that is passed via repeater B or heat energy to air-conditioning object space the supply system cold air or heat air.Indoor heat exchanger 5 and first flow control device (indoor volume control device) 9 is built-in with respectively in indoor set C ~ E.With indoor set C ~ E correspondingly, also indoor heat exchanger 5 and first flow control device 9 are distributed to the Reference numeral of c ~ e.
In addition, near indoor heat exchanger 5, be provided with the volume control device 5-m controlling to carry out the flow of the fluid of heat exchange with cold-producing medium.In addition, below, an example as indoor heat exchanger 5 uses the indoor heat exchanger 5 of air-cooled type to be described, an example as volume control device 5-m uses indoor fan 5-m to be described, but as long as cold-producing medium and other fluids carry out the mode of heat exchange, also other modes such as water-cooled (in this situation, volume control device 5-m is pump) can be adopted.In addition, with indoor set C ~ E correspondingly, also distribute the Reference numeral of c ~ e to indoor fan 5-m.
Indoor heat exchanger 5 carries out heat exchange between the air and thermal medium of the pressure fan supply of fan 5-m indoor, generates and heat air or cooling air for what supply to air-conditioning object space.First flow control device 9 is arranged between second branch 11 of repeater B and indoor heat exchanger 5, freely openable.By this first flow control device 9, adjustment flows into the refrigerant flow of indoor heat exchanger 5.
[characteristic structural of conditioner 100]
In the past, heat exchanger, as recorded in above-mentioned patent document 1, is split, the open and close valves such as magnetic valve is arranged on each heat exchanger, makes the heat transfer area of heat exchanger change situation about controlling more by the opening and closing of open and close valve by the heat exchange amount of outdoor heat exchanger.On the other hand, in conditioner 100, control to employ for the 6th volume control device 26 of the 4th volume control device 22 of middle pressure injected and the heat exchange amount of control room external heat exchanger 3 to make flow path resistance continually varying structure, the heat exchange amount that the flow being flowed into the cold-producing medium of outdoor heat exchanger 3 by adjustment carries out outdoor heat exchanger controls.
By this structure, the 4th volume control device 22 and the 6th volume control device 26 can be configured in parallel.That is, in conditioner 100, owing to connecting the 4th volume control device 22 and the 6th volume control device 26 in parallel, so the pressure loss of cold-producing medium can be reduced, can operate with the state that efficiency is high.In addition, the mode of simplification is, as the 6th volume control device 26, can also be connected in series capillary etc. and magnetic valve, carry out flow adjustment by the opening and closing of magnetic valve.
[needing the situation of injecting to compressor 1]
Fig. 2 represents the result of calculation of the discharge temperature of the ratio relative to R32 of the mix refrigerant of R410A, R32 and HFO1234yf, the mix refrigerant of R32 and HFO1234ze.With reference to Fig. 2, research needs the situation to the injection of compressor 1.In this Fig. 2, transverse axis represents R32 ratio [wt%], and the longitudinal axis represents discharge temperature [DEG C].In addition, suppose that the evaporating temperature that compressor sucks is 5 DEG C, condensation temperature is 45 DEG C, suction SH is 3 DEG C, the heat-insulating efficiency of compressor 1 is 65%.
First, the density being inhaled into the cold-producing medium of compressor 1 when low outer gas heats reduces, and the refrigerant flow in loop reduces.With the reduction of refrigerant flow, heating capacity reduces, thus increases the refrigerant flow of injection, and it is effective that heating capacity is increased.Secondly, the change of the discharge temperature produced by the difference of the cold-producing medium used is studied.When the discharge temperature of cold-producing medium uprises, the bad stability of the encapsulant of compressor 1, the deterioration of refrigerating machine oil, cold-producing medium, thus require discharge temperature to be suppressed to such as less than about 120 DEG C.
As can be seen from Figure 2, when using R32 cold-producing medium with monomer, discharge temperature rising about 20 DEG C of degree compared with R410A.Under these design conditions, discharge temperature is no more than 120 DEG C, but when carrying out low outer gas heat running, high outer gas time the large running of the compression ratio of compressor 1 of cooling operation etc., the possibility of existence more than 120 DEG C.
As can be seen from Figure 2, in order to have with the reliability of R410A same degree carry out Unit Design, when the mix refrigerant of R32 and HFO1234yf, R32 is more than 40wt%, when the mix refrigerant of R32 and HFO1234yf, R32 is more than 15wt%, under these circumstances, needs the countermeasure reducing discharge temperature.Now, by compression midway cold-producing medium injection come cooled compressed midway cold-producing medium be effective.In addition, when allowing to rise about 5 DEG C than R410A, in the mix refrigerant of R32 and HFO1234yf, R32 is more than 60wt%, and in the mix refrigerant of R32 and HFO1234yf, R32 is more than 25wt%.
[operation mode]
Below, to this conditioner 100 perform various running time motion be described.The motion of conditioner 100 has cooling operation, heats running, refrigeration main body running and heat main body and to operate these 4 patterns.
Cooling operation refers to that indoor set only can carry out the operation mode freezed, and carries out freezing or stopping.Heat running and refer to that indoor set only can carry out the operation mode heated, carry out heating or stopping.The running of refrigeration main body refers to the operation mode can selecting cooling and warming by each indoor set, it is large that refrigeration load ratio heats load, outdoor heat exchanger 3 is connected the discharge side of compressor 1, is the operation mode played a role as condenser (radiator).Heat main body running and refer to the operation mode can selecting cooling and warming by each indoor set, heat duty factor refrigeration load large, outdoor heat exchanger 3 is connected the suction side of compressor 1, is the operation mode played a role as evaporimeter.Below, the flowing of the cold-producing medium when situation of not injecting and the injection of each operation mode be described together with P-h line chart.
[cooling operation: the situation of not injecting]
Here, whole situations of freezing of indoor set C, D, E are described.When freezing, four-way switching valve 2 being switched to and makes the flow of refrigerant of discharging from compressor 1 enter outdoor heat exchanger 3.In addition, magnetic valve 8c, 8d, 8e of being connected with indoor set C, D, E open, and 8f, 8g, 8h close.Fig. 3 is the P-h line chart of the migration of the cold-producing medium represented under this cooling operation.
In this condition, the running of compressor 1 is started.The gas refrigerant of low-temp low-pressure is compressed by compressor 1, becomes the gas refrigerant of HTHP and is discharged.In the refrigerant compression process of this compressor 1, to be compressed into the heat-insulating efficiency by compressor with further heating and cooling agent compared with insentrope adiabatic compression cold-producing medium, to represent to the line shown in point (b) with the point (a) of Fig. 3.
Outdoor heat exchanger 3 is flowed into via four-way switching valve 2 from the gas refrigerant of the HTHP of compressor 1 discharge.Now, refrigerant heat outdoor air and cooled, becomes the liquid refrigerant of middle temperature high pressure.When the pressure loss of outdoor heat exchanger 3 is considered in cold-producing medium change in outdoor heat exchanger 3, represent to the straight line close to level slightly tilted shown in point (c) with the point (b) of Fig. 3.
The liquid refrigerant of the middle temperature high pressure of heat exchanger 3 outflow is outdoor separated in second refrigerant pipe arrangement 7, gas-liquid separation device 12, after the cold-producing medium flowed in First Heat Exchanger 17 and in the second bypass pipe arrangement 14b has carried out heat exchange, by second amount control device 13, the cold-producing medium flowed in the second heat exchanger 16 and in the second bypass pipe arrangement 14b carries out heat exchange, and is cooled.The point (c) of Fig. 3 of cooling procedure now represents to point (d).
Liquid refrigerant cooled in first, second heat exchanger 17,16 flows into the second branch 11, and its part is by the second bypass pipe arrangement 14b bypass, and remainder flows into second refrigerant pipe arrangement 7c, 7d, 7e of indoor pusher side.Flowed in second refrigerant pipe arrangement 7c, 7d, 7e of indoor pusher side by the liquid refrigerant of the high pressure of the second branch 11 branch, and flow into first flow control device 9c, 9d, 9e of indoor set C, D, E.And the liquid refrigerant of high pressure is expanded by throttling, reduces pressure in first flow control device 9c, 9d, 9e, becomes the gas-liquid two-phase state of low-temp low-pressure.The change of the cold-producing medium in this first flow control device 9c, 9d, 9e is constant and implement with enthalpy.Cold-producing medium change now represents to the vertical line shown in point (e) with the point (d) of Fig. 3.
Indoor heat exchanger 5c, 5d, 5e is entered from the flow of refrigerant of the gas-liquid two-phase state of the low-temp low-pressure of first flow control device 9c, 9d, 9e outflow.And refrigerant cools room air and being heated, becomes the gas refrigerant of low-temp low-pressure.When the pressure loss is considered in the change of the cold-producing medium in indoor heat exchanger 5c, 5d, 5e, represent to the straight line close to level slightly tilted shown in point (a) with the point (e) of Fig. 3.
The gas refrigerant of the low-temp low-pressure of heat exchanger 5c, 5d, 5e outflow flows into the first branch 10 respectively by magnetic valve 8c, 8d, 8e indoor.In the first branch 10 interflow low-temp low-pressure gas refrigerant with collaborated by the gas refrigerant of the low-temp low-pressure heated in first, second heat exchanger 17,16 of the second bypass pipe arrangement 14b, flow into compressor 1 by the first refrigerant piping 6 and four-way switching valve 2, and compressed.
In addition, outside temperature degree low and from compressor 1 discharge cold-producing medium discharge pressure reduce, for increasing the front and back differential pressure of compressor 1, operation makes the 6th volume control device 26 of outdoor heat exchanger 3 bypass that the refrigerant flow of inflow outdoor heat exchanger 3 is changed, the heat exchange amount of control room external heat exchanger 3.
[cooling operation: carry out the situation of injecting]
The situation that temperature degree is high outside, inferior in the situation that indoor temperature is low, become large at the compression ratio of cold-producing medium, when not injecting, discharge temperature uprises.The action of conditioner 100 is now described.Fig. 4 is the P-h line chart of the migration of the cold-producing medium represented under this cooling operation.In addition, about the flowing of the cold-producing medium in main flow portion, identical with above-mentioned cooling operation, the situation of not injecting, thus omit the description.
When injecting to compressor 1, the 5th volume control device 24 of injection pipe arrangement 23 being controlled to and opening.So a part for liquid refrigerant cooled in outdoor heat exchanger 3 is branched to injection pipe arrangement 23, is depressurized in the 5th volume control device 24.Cold-producing medium change now represents to point (f) with the point (c) of Fig. 4.The cold-producing medium be depressurized in the 5th volume control device 24 is injected into by injection pipe arrangement 23 cold-producing medium compressing midway in compressor 1.Accordingly, reduce from the discharge temperature of the cold-producing medium of compressor 1 discharge.
[heating running: the situation of not injecting]
Here, whole situations about heating of indoor set C, D, E are described.When carrying out heating running, four-way switching valve 2 is switched to and makes the cold-producing medium of discharging from compressor 1 flow into the first branch 10.In addition, magnetic valve 8c, 8d, 8e of being connected with indoor set C, D, E close, and 8f, 8g, 8h open.Fig. 5 represents that this heats the P-h line chart of the migration of the cold-producing medium under operating.
In this condition, the running of compressor 1 is started.The gas refrigerant of low-temp low-pressure is compressed by compressor 1, becomes the gas refrigerant of HTHP and is discharged.The refrigerant compression process of this compressor represents to the line shown in point (b) with the point (a) of Fig. 5.
The first branch 10 is flowed into by four-way switching valve 2 and second refrigerant pipe arrangement 7 from the gas refrigerant of the HTHP of compressor 1 discharge.The gas refrigerant flowing into the HTHP of the first branch 10 is branched in the first branch 10, flows into indoor heat exchanger 5c, 5d, 5e by magnetic valve 8f, 8g, 8h.And refrigerant cools room air and being heated, becomes the liquid refrigerant of middle temperature high pressure.The change of the cold-producing medium in indoor heat exchanger 5c, 5d, 5e represents to the straight line close to level slightly tilted shown in point (c) with the point (b) of Fig. 5.
The liquid refrigerant of the middle temperature high pressure of heat exchanger 5c, 5d, 5e outflow flows into first flow control device 9c, 9d, 9e indoor, collaborates, then flow into the 3rd volume control device 15 in the second branch 11.And the liquid refrigerant of high pressure is expanded by throttling, reduces pressure in first flow control device 9c, 9d, 9e and the 3rd volume control device 15, the 4th volume control device 22, becomes the gas-liquid two-phase state of low-temp low-pressure.Cold-producing medium change now represents to the vertical line shown in point (d) with the point (c) of Fig. 5.
The flow of refrigerant of gas-liquid two-phase state of the low-temp low-pressure flowed out from the 4th volume control device 22 enters outdoor heat exchanger 3, refrigerant cools outdoor air and being heated, and becomes the gas refrigerant of low-temp low-pressure.Cold-producing medium change in outdoor heat exchanger 3 represents to the straight line close to level slightly tilted shown in point (a) with the point (d) of Fig. 5.The gas refrigerant of the low-temp low-pressure of heat exchanger 3 outflow outdoor flows into compressor 1 by four-way switching valve 2 and is compressed.
In addition, when high the and suction pressure of temperature degree rises outside, in order to increase the front and back differential pressure of compressor 1, operation makes the 6th volume control device 26 of outdoor heat exchanger 3 bypass and makes the refrigerant flow change of inflow outdoor heat exchanger 3 carry out the heat exchange amount of control room external heat exchanger 3.
[heating running: carry out the situation of injecting]
Low and the action that the is conditioner 100 needing the compression ratio of the front and back of the situation of heating capacity, compressor 1 to become when discharge temperature uprises when injecting greatly and not of external temperature degree is described.Fig. 6 represents that this heats the P-h line chart of the migration of the cold-producing medium in running.In addition, about the flowing of the cold-producing medium in main flow portion, with above-mentioned heat operate, the situation of not injecting is substantially identical, thus to omit the description.
In addition, when not injecting, the balance of the throttling of the 3rd volume control device 15, the 4th volume control device 22 is arbitrary, but when injecting, make the pressure increase of the cold-producing medium injected to compressor 1, easily carry out flow adjustment, thus the pressure differential the best outlet (middle pressure) from discharge pressure to the 3rd volume control device 15 adopts about 1MPa, utilize the adjustment of the 4th volume control device 22 to flow into the refrigerant flow of outdoor heat exchanger 3.
Circulate in indoor set C, D, E and the part returning the cold-producing medium (point (e) of Fig. 6) of off-premises station A flows into the 4th volume control device 22, remaining cold-producing medium flows into the 5th volume control device 24.The cold-producing medium flowing into the main flow of the 4th volume control device 22 is depressurized (point (d)) in the 4th volume control device 22, and flows into outdoor heat exchanger 3.On the other hand, the cold-producing medium being branched to injection pipe arrangement 23 is depressurized (point (f)) in the 5th volume control device 24, and is injected into compressor 1.The cold-producing medium of gas-liquid two-phase state is injected into compressor 1, and accordingly, refrigerant flow increases, and discharge temperature reduces, and in addition, heating capacity increases.
[refrigeration main body running: the situation of not injecting]
Here, indoor set C, D to be freezed and the situation that indoor set E heats is described.In this case, four-way switching valve 2 is switched to make the flow of refrigerant of discharging from compressor 1 enter outdoor heat exchanger 3.In addition, magnetic valve 8c, 8d, 8h of being connected indoor set C, D, E open, and 8f, 8g, 8e close.Fig. 7 is the P-h line chart of the migration of the cold-producing medium represented in the running of this refrigeration main body.
In this condition, the running of compressor 1 is started.The gas refrigerant of low-temp low-pressure is compressed by compressor 1, becomes the gas refrigerant of HTHP and is discharged.The refrigerant compression process of this compressor 1 represents to the line shown in point (b) with the point (a) of Fig. 7.
Outdoor heat exchanger 3 is flowed into via four-way switching valve 2 from the gas refrigerant of the HTHP of compressor 1 discharge.Now, remainingly in outdoor heat exchanger 3 heat required heat, refrigerant heat outdoor air and cooled, become the gas-liquid two-phase state of middle temperature high pressure.Cold-producing medium change in outdoor heat exchanger 3 represents to the straight line close to level slightly tilted shown in point (c) with the point (b) of Fig. 7.
The gas-liquid two-phase cold-producing medium of the middle temperature high pressure of heat exchanger 3 outflow outdoor, by second refrigerant pipe arrangement 7, flows into gas-liquid separation device 12.And, in gas-liquid separation device 12, be separated into gas refrigerant (point (d)) and liquid refrigerant (point (e)).
Gas refrigerant (point (d)) separated in gas-liquid separation device 12 flows into via the first branch 10, magnetic valve 8h the indoor heat exchanger 5e carrying out heating.And refrigerant heat room air and cooled, becomes the liquid refrigerant of middle temperature high pressure.The change of the cold-producing medium in indoor heat exchanger 5e represents to the straight line close to level slightly tilted shown in point (f) with the point (d) of Fig. 7.
On the other hand, liquid refrigerant (point (e)) separated in gas-liquid separation device 12 flows into First Heat Exchanger 17, carries out heat exchange and be cooled with the low pressure refrigerant flowed in the second bypass pipe arrangement 14b.The change of the cold-producing medium in First Heat Exchanger 17 represents to the approximate horizontal straight line shown in point (g) with the point (e) of Fig. 7.
The cold-producing medium (point (f)) flowed out from the indoor heat exchanger 5e that carries out heating is by first flow control device 9e, from First Heat Exchanger 17 flow out cold-producing medium (point (g)) by second amount control device 13, second heat exchanger 16, in the second branch 11 collaborate (point (h)).A part for the liquid refrigerant at interflow is by the second bypass pipe arrangement 14b bypass, and first flow control device 9c, 9d of indoor set C, the D freezed are carried out in remaining inflow.And the liquid refrigerant of high pressure is expanded by throttling, reduces pressure in first flow control device 9c, 9d, becomes the gas-liquid two-phase state of low-temp low-pressure.The change of the cold-producing medium in this first flow control device 9c, 9d is carried out so that enthalpy is constant.Cold-producing medium change now represents to the vertical line shown in point (i) with the point (h) of Fig. 7.
Indoor heat exchanger 5c, 5d of carrying out freezing is flowed into from the cold-producing medium of the gas-liquid two-phase state of the low-temp low-pressure of first flow control device 9c, 9d outflow.And refrigerant cools room air and being heated, becomes the gas refrigerant of low-temp low-pressure.The change of the cold-producing medium in indoor heat exchanger 5c, 5d represents to the straight line close to level slightly tilted shown in point (a) with the point (i) of Fig. 7.
The gas refrigerant of the low-temp low-pressure of heat exchanger 5c, 5d outflow flows into the first branch 10 respectively by magnetic valve 8c, 8d indoor.The gas refrigerant of low-temp low-pressure collaborated in the first branch 10 and being collaborated by the gas refrigerant of the low-temp low-pressure heated in first, second heat exchanger 17,16 of the second bypass pipe arrangement 14b, and flow into compressor 1 by the first refrigerant piping 6 and four-way switching valve 2, and compressed.
In addition, outside low, the discharge pressure of temperature degree reduce and heating capacity deficiency when, in order to increase the front and back differential pressure of compressor 1, operation makes the 6th volume control device 26 of outdoor heat exchanger 3 bypass and the refrigerant flow of inflow outdoor heat exchanger 3 is changed, and carrys out the heat exchange amount of control room external heat exchanger 3.
[refrigeration main body running: carry out the situation of injecting]
The compression ratio of cold-producing medium is become greatly, the action of conditioner 100 when discharge temperature uprises when not injecting is described.Fig. 8 is the P-h line chart of the migration of the cold-producing medium represented in the running of this refrigeration main body.In addition, about the flowing of the cold-producing medium in main flow portion, substantially identical with the situation of not injecting, thus omit the description.
When injecting to compressor 1, the 5th volume control device 24 of injection pipe arrangement 23 being controlled to and opening.So a part for cold-producing medium cooled in outdoor heat exchanger 3 is branched to injection pipe arrangement 23, and is depressurized in the 5th volume control device 24 (point (j) of Fig. 8).The cold-producing medium of the gas-liquid two-phase be depressurized in the 5th volume control device 24, by injection pipe arrangement 23, is injected into the cold-producing medium of compression midway in compressor 1.Accordingly, reduce from the discharge temperature of the cold-producing medium of compressor 1 discharge.
[heating main body running: the situation of not injecting]
Here, indoor set C is freezed, situation that indoor set D, E heat is described.In this case, four-way switching valve 2 is switched to make the cold-producing medium of discharging from compressor 1 flow into the first branch 10.In addition, magnetic valve 8f, 8d, 8e of being connected with indoor set C, D, E close, and 8c, 8g, 8h open.In addition, in order to reduce the pressure differential of indoor set C and the outdoor heat exchanger 3 carrying out freezing, the evaporating pressure that volume control device 22 is controlled so as to standard-sized sheet or second refrigerant pipe arrangement 7 becomes about 0 DEG C with saturation temperature conversion.Fig. 9 represents that this heats the P-h line chart of the migration of the cold-producing medium in main body running.
In this condition, the running of compressor 1 is started.The gas refrigerant of low-temp low-pressure is compressed by compressor 1, becomes the gas refrigerant of HTHP and is discharged.The refrigerant compression process of this compressor represents to the line shown in point (b) with the point (a) of Fig. 9.
The first branch 10 is flowed into via four-way switching valve 2 and second refrigerant pipe arrangement 7 from the gas refrigerant of the HTHP of compressor 1 discharge.The gas refrigerant flowing into the HTHP of the first branch 10 is branched in the first branch 10, is flowed into indoor heat exchanger 5d, 5e of carrying out indoor set D, the E heated by magnetic valve 8g, 8h.And refrigerant heat room air and cooled, becomes the liquid refrigerant of middle temperature high pressure.The change of the cold-producing medium in indoor heat exchanger 5d, 5e represents to the straight line close to level slightly tilted shown in point (c) with the point (b) of Fig. 9.
The liquid refrigerant of the middle temperature high pressure of heat exchanger 5d, 5e outflow flows into first flow control device 9d, 9e indoor, and collaborates in the second branch 11.In the second branch 11, a part for the liquid refrigerant of the high pressure at interflow flows into the first flow control device 9c be connected with the indoor set C carrying out freezing.And the liquid refrigerant of high pressure is expanded by throttling, reduces pressure in first flow control device 9c, becomes the gas-liquid two-phase state of low-temp low-pressure.Cold-producing medium change now represents to the vertical line shown in point (d) with the point (c) of Fig. 9.
The low-temp low-pressure flowed out from first flow control device 9c and the cold-producing medium of gas-liquid two-phase state flow into and carry out the indoor heat exchanger 5c that freezes.And refrigerant cools room air and being heated, becomes the gas refrigerant of low-temp low-pressure.Cold-producing medium change now represents to the straight line close to level slightly tilted shown in point (e) with the point (d) of Fig. 9.The gas refrigerant of the low-temp low-pressure of heat exchanger 5c outflow flows into the first refrigerant piping 6 by magnetic valve 8c indoor.
On the other hand, the remainder flowing into the liquid refrigerant of the high pressure of the second branch 11 from indoor heat exchanger 5d, 5e of carrying out heating flows into the 3rd volume control device 15.And the liquid refrigerant of high pressure by throttling and expand (decompression), becomes the gas-liquid two-phase state of low-temp low-pressure in the 3rd volume control device 15.Cold-producing medium change now represents to the vertical line shown in point (f) with the point (c) of Fig. 9.The low-temp low-pressure flowed out from the 3rd the volume control device 15 and cold-producing medium of gas-liquid two-phase state flows into the first refrigerant piping 6, and collaborates (point (g) of Fig. 9) with the vaporous cold-producing medium of the low-temp low-pressure flowed into from the indoor heat exchanger 5c carrying out freezing.
In the first refrigerant piping 6 interflow low-temp low-pressure and the flow of refrigerant of gas-liquid two-phase state enters outdoor heat exchanger 3.And cold-producing medium air heat absorption outdoor, becomes the gas refrigerant of low-temp low-pressure.Cold-producing medium change now represents to the straight line close to level slightly tilted shown in point (a) with the point (g) of Fig. 9.The gas refrigerant of the low-temp low-pressure of heat exchanger 3 outflow outdoor flows into compressor 1 by four-way switching valve 2, and is compressed.
[heating main body running: carry out the situation of injecting]
The compression ratio of cold-producing medium is become greatly, the action of conditioner 100 when discharge temperature uprises when not injecting is described.Figure 10 represents that this heats the P-h line chart of the migration of the cold-producing medium in main body running.In addition, about the flowing of the cold-producing medium in main flow portion, identical with the situation of not injecting, thus omit the description.
In addition, the throttling of the 4th volume control device 22 is to make the pressure increase of the cold-producing medium injected to compressor 1 and guarantee to carry out the ability of the indoor set freezed, being controlled so as to about 0 DEG C with the evaporating temperature of the first refrigerant piping 6.Now, to circulate and the part flowing into the cold-producing medium (point (h) of Figure 10) of the gas-liquid two-phase of off-premises station flows into the 4th volume control device 22 in indoor set, remaining cold-producing medium flows into the 5th volume control device 24.The cold-producing medium flowing into the main flow of the 4th volume control device 22 is depressurized (point (i) of Figure 10), and flows into outdoor heat exchanger 3.On the other hand, the cold-producing medium be branched is depressurized (point (j)) in the 5th volume control device 24, and is injected into compressor 1.The cold-producing medium of gas-liquid two-phase is injected into compressor, and accordingly, refrigerant flow increases, and discharge temperature reduces, and in addition, heating capacity increases.
[carrying out the situation about operating that defrosts]
Here, on outdoor heat exchanger 3 frost and carry out defrost running situation study.In order to excellent in efficiency defrost, need the temperature difference of the temperature reducing outer temperature degree and cold-producing medium, prevent heat radiation, shorten defrosting time and shorten the time that outside gas dispels the heat.Especially, the mix refrigerant of R32 or R32 and HFO1234yf, HFO1234ze cold-producing medium is compared with the situation of R410A cold-producing medium, and discharge temperature rises, thus reduces discharge temperature by injection, and it is effective for making refrigerant flow increase and defrosting ability is improved.
[other loop structures of conditioner 100]
As mentioned above, in conditioner 100, regardless of operation mode, volume control device (the 4th volume control device 22, the 6th volume control device 26) impact on the pressure loss can be suppressed, and, the heat exchange amount that can carry out outdoor heat exchanger 3 controls and injection control, and can reduce the discharge temperature of compressor 1, and compressor 1 can operate with the state that reliability is high.
In addition, in conditioner 100, freeze main body running time, heat main body running time, when injecting, according to loading condition, the cold-producing medium of the gas-liquid two-phase that injected gas composition is many.In order to reliably reduce discharge temperature, the side that preferred liquid measure is many.Accordingly, conditioner 100 also can adopt the loop structure being provided with gas-liquid separation device 32 and the 3rd heat exchanger 33 as illustrated in fig. 11.Figure 11 is the refrigerant loop figure of another example of the refrigerant loop structure representing conditioner 100.
Gas-liquid separation device 32 is arranged on check-valves 18 and check-valves 21 and the 4th volume control device 22 and between the 5th volume control device 24 and the 5th volume control device 26, that is, is arranged on the link position of injection pipe arrangement 23.Gas-liquid separation device 32 is for becoming the refrigerant branch of middle pressure condition with the cold-producing medium of main flow flowing and the cold-producing medium carrying out injecting.And, injection pipe arrangement 23 is connected to the liquid phase part of gas-liquid separation device 32.3rd heat exchanger 33 be arranged on check-valves 18, main flow between check-valves 21 and gas-liquid separation device 32 cold-producing medium and in the position of injecting the cold-producing medium flowed in pipe arrangement 23 and can carry out heat exchange.
By arranging gas-liquid separation device 32 and the 3rd heat exchanger 33, the ability of the evaporimeter of conditioner 100 is improved further, and cooling and warming performance improves further.
[controls of the executing agencies such as compressor 1]
Finally, the control of the executing agency of the inscape and compressor 1 etc. of conditioner 100 is studied.In conditioner 100, as mentioned above, the thermometer 54 of the pressure gauge 53 of pressure, the discharge temperature of mensuration cold-producing medium in the pressure gauge 51 with the discharge pressure measuring cold-producing medium, the pressure gauge 52 measuring suction pressure, mensuration.In addition, also can replace pressure gauge 53 set temperature meter, carry out conversion pressure from measured saturation temperature and calculate.
The rotating speed of the outdoor fan 3-a that the driving frequency of compressor 1, outdoor heat exchanger 3 have is controlled so as to the measured value of reference pressure meter 51,52 and becomes regulation ability with the cooling and warming ability of each indoor set.Now, also whether regulation ability can be reached from the ability of the front and back pressure presumption indoor set of compressor 1.This is because, in general the capacity of indoor set is designed in the condensation temperature specified, evaporating temperature (when such as heating, condensation temperature is 40 DEG C, during refrigeration, evaporating temperature is 10 DEG C) under can play necessary ability, thus by controlling discharge pressure, the suction pressure of compressor 1, the cooling and warming ability of indoor set can be adjusted.
In conditioner 100, as mentioned above, the control device 50 with memory 50a is set respectively in off-premises station A and repeater B.Control device 50 can be connected by wireless or wire communication each other.In this configuration, control device 50 is arranged on off-premises station A, repeater B respectively, but control member is concentrated on 1 unit, and between each unit, intercommunication controlling value carries out the control of executing agency, also no problem.In addition, in the following description, sometimes 2 control device 50 are generically and collectively referred to as control device 50.
Control device 50 carries out the drived control such as running, stopping of the fan electromotor of indoor fan 5c-m ~ 5e-m based on the setting of the remote controller of indoor set C ~ E and the Current Temperatures of indoor.In addition, control device 50, according to the running capacity of the cooling and warming of indoor set C ~ E, according to operation mode, carries out the aperture of the volume control device being in repeater B, the switching of magnetic valve.And control device 50 carries out the drived control of the driving of compressor 1, the switching of four-way switching valve 2, the fan electromotor of outdoor fan 3-a.
Figure 12 is the flow chart of the control flow that heat exchange amount controls and injection controls of the outdoor heat exchanger 3 represented performed by conditioner 100.Figure 13 is the flow chart of the control flow representing the details that the heat exchange amount of outdoor heat exchanger 3 controls.Figure 14 is the flow chart of the control flow representing the details that injection controls.Figure 15 is the refrigerant loop figure of the another example of the refrigerant loop structure representing conditioner 100.Based on Figure 12 ~ 15, control the heat exchange amount of the outdoor heat exchanger 3 performed by conditioner 100 and inject control to be described.
First, the heat exchange amount of outdoor heat exchanger 3 is controlled, be described with reference to Figure 12, Figure 13.When conditioner 100 starts running (the step S1 of Figure 12), the heat exchange amount that control device 50 performs outdoor heat exchanger 3 controls (the step S2 of Figure 12, the step S101 of Figure 13).The heat exchange amount of outdoor heat exchanger 3 uses open and close valve 27-1,27-2 before and after outdoor fan 3-a, the outdoor heat exchanger 3 shown in following Figure 15,27-3, the 6th volume control device 26, the 4th volume control device 22 to control.
Control device 50 judges that what (step S102 of Figure 13) current be by the operation mode selected.And, control device 50 start to by the corresponding control (the step S103 of Figure 13, step S121) of the operation mode selected.When cooling operation or refrigeration main body operation mode are selected, control device 50 starts the control (the step S104 ~ step S119 of Figure 13) of each executing agency based on discharge pressure.On the other hand, when selecting heat running or heat main body operation mode, control device 50 starts the control (the step S121 ~ step S136 of Figure 13) of each executing agency based on suction pressure.
In addition, in step S105 ~ step S112, the step S113 ~ step S119, step S121 ~ step S129, step S130 ~ step S136 of Figure 13, the priority of the executing agency when controlling value of each executing agency changes also can front or rear, but the desired value of setting discharge pressure or suction pressure, apply gain to the difference with currency, change the controlling value of each executing agency.In addition, also can change the executing agency of more than 2 simultaneously.
And, when cooling operation or the running of refrigeration main body of low outer gas, when carrying out the flow-control of outdoor heat exchanger 3, in the heat-transfer pipe of outdoor heat exchanger 3, there is a large amount of liquid refrigerants, there is the possibility of the lack of refrigerant of refrigerant loop entirety.Therefore, as shown in figure 15, the gateway of the cold-producing medium of outdoor heat exchanger 3 is divided into multiple mouth, in the configuration of the front and back of an outdoor heat exchanger 3-2, cold-producing medium is discharged to bypass pipe arrangement 14c and the open and close valve 27-3 of reservoir 4 from open and close valve 27-1,27-2 and outdoor heat exchanger 3-2.And, when being judged as the short of refrigerant in loop, if close open and close valve 27-1 and 27-2, opening open and close valve 27-3, then the cold-producing medium be trapped in outdoor heat exchanger 3-2 can be supplied in refrigerant loop.
In addition, it is the situation that the heat exchange amount be in outdoor heat exchanger 3 becomes too much that the 6th volume control device 26 carries out by-pass governing, even if close open and close valve 27-1 and 27-2, the heat exchange amount in outdoor heat exchanger 3 is also not enough.In addition, when heating running, heating main body running, drive the cold-producing medium needed for circulation few, thus do not need outdoor heat exchanger 3 is reduced by half, also when the control of executing agency, also can skip the step S126 of Figure 13, S127, S132, S133.
Below, the injection improved for heating capacity, discharge temperature reduces is controlled, is described with reference to Figure 12, Figure 14.Control device 50, when the heat exchange amount terminating outdoor heat exchanger 3 controls, performs injection and controls (the step S3 of Figure 12, the step S201 of Figure 14).
First, in order to inject, need to make the pressure in the discharge chambe of the pressure ratio compressors 1 of injection pipe arrangement 23 high.When cooling operation or the running of refrigeration main body, flow into the pressure approximately discharge pressure of the cold-producing medium of the 5th volume control device 24 of injection pipe arrangement 23, thus do not need pressure in control, as long as make the 4th volume control device 22 standard-sized sheet (the step S202 ~ step S205 of Figure 14).But, when the heat exchange amount in order to carry out outdoor heat exchanger 3 controls and controls the 4th volume control device 22, keep its aperture.
On the other hand, when heating running or heat main body running, when making the 4th volume control device 22 standard-sized sheet, middle pressure becomes roughly the same with suction pressure, there is the possibility can not carrying out necessary injection.Therefore, when heating running, operate the 4th volume control device 22, to press to the mode of setting (being such as scaled about 15 DEG C with the pressure differential saturation temperature of discharge pressure) in making, when heating main body running, consider that indoor set carries out the situation of freezing, converting that the mode that becomes 0 DEG C ~ about 5 DEG C carries out setting with the saturation temperature saturation temperature of middle pressure can (the step S206 ~ step S211 of Figure 14).
Below, such as, when the discharge temperature (measured value of thermometer 54) of compressor 1 becomes setting (such as more than 110 DEG C), the discharge temperature that operation the 5th volume control device 24 carries out being implemented by injection controls (the step S212 of Figure 14).The mode that the control of discharge temperature now such as becomes 20 DEG C ~ 50 DEG C with the difference of discharge temperature and condensation temperature carries out controlling.
Here, the situation that the heat exchange amount of outdoor heat exchanger 3 controls and generation injection controls is studied.Figure 16 is the flow chart of control flow when representing the control method selecting conditioner 100.The condition needing the heat exchange amount of outdoor heat exchanger 3 to control be do not need the loading condition according to indoor, condition that outer gas temperature conditions makes outdoor fan 3-a full speed operation.Now, compression ratio is little, and discharge temperature is not very high.In addition, heating running, heating in main body running, be also the condition that outer temperature degree is high, thus also can not need heating capacity is increased, need not inject.
On the other hand, the condition needing injection is the condition that compression ratio becomes large, outdoor fan 3-a full speed operation, and the 6th volume control device 26 becomes full cut-off, reduces compression ratio ground as much as possible and controls.It can thus be appreciated that, as shown in figure 16, also can control according to the heat exchange amount of indoor loading condition, outer gas temperature conditions switching chamber external heat exchanger 3 and injection control.
[table 1]
Decision condition
Table 1 represents an example of the decision method when temperature degree modification control method in addition.In cooling operation, at the threshold value x of temperature degree in addition 1the mode that [DEG C] becomes between 30 DEG C to 40 DEG C sets, outer temperature degree as one of service data uprises and the discharge pressure circulated uprises when, be judged to be that discharge temperature uprises, carry out injection to control, when in addition, the heat exchange amount carrying out outdoor heat exchanger 3 controls.In general, under temperature degree is greater than the situation of 30 DEG C outside, is difficult to consideration and utilizes indoor set to heat, thus in the running of refrigeration main body, the heat exchange amount only carrying out outdoor heat exchanger 3 controls.
On the other hand, heating, heating in main body running, such as to make x 2[DEG C], x 3the mode that [DEG C] becomes 0 DEG C to about 10 DEG C respectively presets, and when outer temperature degree is high, suction pressure is high, is judged as that discharge temperature is low and heating capacity sufficient, can carries out the control of outdoor heat exchanger 3.In addition, when low, the suction pressure of temperature degree is low outside, be judged as that discharge temperature is high and heating capacity is also not enough, injection can be carried out and control.In addition, except for the outer beyond temperature degree, pressure in indoor load (operating number of the cooling and warming of indoor temperature, indoor set), conditioner, temperature, compressor frequency can also be added determinating reference as service data, can more stable control be carried out.
Above, according to conditioner 100, when arbitrary operation mode, can both reduce discharge temperature, compressor 1, with while the state running that reliability is high, can realize the running of the excellent in efficiency corresponding to the load of indoor.
Embodiment 2
Figure 17 is the summary loop structure figure of an example of the refrigerant loop structure of the conditioner 200 representing embodiments of the present invention 2.Based on Figure 17, conditioner 200 is described.In addition, preferably in 2, by with the difference of above-mentioned embodiment 1 centered by be described, about the part that refrigerant loop structure etc. is identical with embodiment 1, omit the description.In addition, about each operation mode performed by conditioner 200 and the control under each operation mode, identical with the conditioner 100 of embodiment 1, then omit the description.
The structure of the injection pipe arrangement 23 in the off-premises station A of conditioner 200 and the 3rd bypass pipe arrangement 25 is different from the conditioner 100 of embodiment 1.Conditioner 200 becomes the heat exchange amount control of switching chamber external heat exchanger 3, the structure of injection flow-control.
The injection pipe arrangement 23 of embodiment 2 is the pipe arrangements arranged in order to the cold-producing medium of middle pressure is expelled to compressor 1 in the same manner as the injection pipe arrangement 23 of embodiment 1.But the injection pipe arrangement 23 of embodiment 2 is different from the injection pipe arrangement 23 of embodiment 1, be connected the illustrated injection port of omission of compressor 1 from the 3rd bypass pipe arrangement 25 branch.And, the injection pipe arrangement 23 of embodiment 2 is provided with open and close valve 24-2.The injection flow of this open and close valve 24-2 by being controlled to compressor 1 by controlling opening and closing.
3rd bypass pipe arrangement 25 is the pipe arrangements in order to make outdoor heat exchanger 3 bypass arrange.But on the 3rd bypass pipe arrangement 25, being provided with in parallel with the 4th volume control device 22 can volume control device 24-1 (26-1), the open and close valve 26-2 of bypass flow of control room external heat exchanger 3.
Above, according to conditioner 200, in the same manner as the conditioner 100 of embodiment 1, when arbitrary operation mode, reduce discharge temperature, compressor 1 with while the state running that reliability is high, can realize the running of the excellent in efficiency corresponding to the load of indoor.In addition, according to conditioner 200, can control according to the heat exchange amount of object switching chamber external heat exchanger 3, inject flow-control.
Embodiment 3
Figure 18 is the summary loop structure figure of an example of the refrigerant loop structure of the conditioner 300 representing embodiments of the present invention 3.Based on Figure 18, conditioner 300 is described.In addition, preferably in 3, by with the difference of above-mentioned embodiment 1 and embodiment 2 centered by be described, about the part that refrigerant loop structure etc. is identical with embodiment 1 and embodiment 2, omit the description.In addition, about each operation mode performed by conditioner 300 and the control under each operation mode, identical with the conditioner 100 of embodiment 1, thus omit the description.
Conditioner 300 in refrigeration, refrigeration main body, heat, under whole operation modes of heating main body, make the direction of the cold-producing medium of the outdoor heat exchanger 3 of inflow off-premises station A be constant direction, but different from the conditioner 100 of embodiment 1.Thereupon, the setting position of the 4th volume control device 22, check-valves 21 is different with the conditioner 100 of embodiment 1.In addition, be provided with check-valves 28, check-valves 29, check-valves 30, this point of check-valves 31, different from the conditioner 100 of embodiment 1.
In addition, the second connecting pipings 60b is connected between check-valves 28 and the 4th volume control device 22.And second refrigerant pipe arrangement 7 is connected between four-way switching valve 2 and check-valves 28 and between outdoor heat exchanger 3 and check-valves 18.And injection pipe arrangement 23 connects the injection port of the second connecting pipings 60b and compressor 1.The second refrigerant pipe arrangement 7 of the upstream side of check-valves 18 is connected the injection pipe arrangement 23 between check-valves 30 and the 5th volume control device 24 by pipe arrangement 60c.
4th volume control device 22 be connected outdoor heat exchanger 3 relative on another pipe arrangement the pipe arrangement be connected with check-valves 18 (downstream of outdoor heat exchanger).Check-valves 28 is arranged between four-way switching valve 2 and the 4th volume control device 22, only allows the circulation to the cold-producing medium of the 4th volume control device 22 from four-way switching valve 2.Check-valves 21 is arranged on the second connecting pipings 60b of being connected between check-valves 28 and the 4th volume control device 22, only allows the circulation to the cold-producing medium of the 4th volume control device 22 from the first refrigerant piping 6.Check-valves 29 is arranged on the second refrigerant pipe arrangement 7 connected between four-way switching valve 2 and check-valves 28 and between outdoor heat exchanger 3 and check-valves 18, only allows the downstream of heat exchanger 3 outdoor to the circulation of the cold-producing medium of four-way switching valve 2.
The injection pipe arrangement 23 of the upstream side of the 5th volume control device 24 is provided with check-valves 30.This check-valves 30 is the injections for heating, heating during main body running, only allows the circulation to the cold-producing medium of injection pipe arrangement 23 from the first refrigerant piping 6.The pipe arrangement 60c of the upstream side of the 5th volume control device 24 is provided with check-valves 31.The injection of this check-valves 31 for freezing, freezing during main body running, only allows the downstream of heat exchanger 3 outdoor to the circulation of the cold-producing medium of injection pipe arrangement 23.
By adopting such structure, in conditioner 300, the flowing of the cold-producing medium in outdoor heat exchanger 3 can be made to become constant direction.And, if regardless of operation mode, all make the flowing of cold-producing medium and air become convection current, then can operate with the little state excellent in efficiency of the temperature difference of air and cold-producing medium.In addition, regardless of condenser, evaporimeter, the flow direction of operation cold-producing medium is to become the effect of convection current, good especially with regard to the mix refrigerant of thermograde produced because of zeotropy.
Figure 19 is the summary loop structure figure of another example that the refrigerant loop of the conditioner 400 representing embodiments of the present invention 3 is formed.Based on Figure 19, conditioner 400 is described.In addition, about each operation mode performed by conditioner 100 and the control under each operation mode, identical with the conditioner 100 of embodiment 1, thus omit the description.
In conditioner 400, about check-valves 18, the check-valves 21 of conditioner 300, be made up of the check-valves 18-1 be connected in series and check-valves 18-2 and check-valves 21-1 and 21-2 respectively.And in conditioner 400, the connecting pipings between check-valves 18-1,18-2 is connected in the mode of collaborating in the connecting pipings between check-valves 21-1,21-2.In addition, in conditioner 400, be configured with gas-liquid separation device 32, the 3rd heat exchanger 33 in the same manner as the structure shown in Figure 11.
By adopting such structure, in conditioner 400, by the reliable reduction of discharge temperature, the improvement of evaporator capacity, cooling and warming performance improves.
Above, according to the conditioner of embodiment 3, in the same manner as the conditioner 100 of embodiment 1, when arbitrary operation mode, discharge temperature can both be reduced, compressor 1, with while the state running that reliability is high, can realize the running of the excellent in efficiency corresponding to the load of indoor.In addition, according to the conditioner of embodiment 3, the running corresponding to loop structure can be realized.
Embodiment 4
Figure 20 is the summary loop structure figure of an example of the refrigerant loop structure of the conditioner 500 representing embodiments of the present invention 4.Based on Figure 20, conditioner 500 is described.In addition, preferably in 4, by with the difference of above-mentioned embodiment 1 ~ 3 centered by be described, about the part that refrigerant loop structure etc. is identical with embodiment 1 ~ 3, omit the description.In addition, about each operation mode performed by conditioner 500 and the control under each operation mode, identical with the conditioner 100 of embodiment 1, then omit the description.
In conditioner 500, in repeater B, be provided with Intermediate Heat Exchanger 40a, 40b.In each Intermediate Heat Exchanger 40a, 40b, cold-producing medium with carry out heat exchange by the driven second refrigerant of pump 41a, 41b, obtain hot water, cold water.In addition, use the mixed liquor etc. of the additive that the mixed liquor of anti-icing fluid (refrigerating medium), water, anti-icing fluid and water, water and anticorrosion ability are high as second refrigerant, flow in thick line portion in the drawings.That is, conditioner 500 is configured to 2 refrigerant loops carries out heat exchange in Intermediate Heat Exchanger 40a, 40b.
Heat from Intermediate Heat Exchanger 40a, 40b of repeater B to indoor set C ~ E is conducted through refrigerating medium and carries out.That is, supply refrigerating medium by second indoor pusher side refrigerant piping 7c ~ 7e to indoor set C ~ E from repeater B, carry out freezing, heating, refrigerating medium returns repeater B by first indoor pusher side refrigerant piping 6c ~ 6e.In addition, second indoor pusher side refrigerant piping 7c ~ 7e is almost identical with the density of the refrigerating medium in first indoor pusher side refrigerant piping 6c ~ 6e, thus both thicknesses of pipe arrangement also can be identical.
In addition, in repeater B, be provided with the magnetic valve 42c ~ 42h selecting the second indoor pusher side refrigerant piping 7c ~ 7e of indoor set C ~ E and the connection of Intermediate Heat Exchanger 40a, 40b.In addition, in repeater B, be provided with the magnetic valve 42i ~ 42n selecting the first indoor pusher side refrigerant piping 6c ~ 6e of indoor set C ~ E and the connection of Intermediate Heat Exchanger 40a, 40b.And, between magnetic valve 42c ~ 42h and indoor set C ~ E, be provided with volume control device 43c ~ 43e that adjustment flows into the flow of the refrigerating medium of indoor set C ~ E.
In addition, here, be described for the situation with two Intermediate Heat Exchangers 40a, 40b, but the number of units of Intermediate Heat Exchanger is not limited thereto, as long as cooling and/or heating second refrigerant can be configured to, it is all right that several Intermediate Heat Exchanger is set.In addition, each pump 41a, 41b are not limited to one, also can use by pump that is in parallel, that in series arrange multiple low capacity.
In conditioner 500, all carry out at indoor set C ~ E in the cooling operation freezed, Intermediate Heat Exchanger 40a, 40b, in order to obtained cold water, play a role as evaporimeter.The P-h line chart of kind of refrigeration cycle side is now identical with Fig. 3 when not injecting, identical with Fig. 4 in the case of injection.In addition, in conditioner 500, that all carries out heating at indoor set C ~ E heats in running, and Intermediate Heat Exchanger 40a, 40b, in order to obtained hot water, play a role as radiator.The P-h line chart of kind of refrigeration cycle side is now identical with Fig. 5 when not injecting, identical with Fig. 6 in the case of injection.
And in conditioner 500, when utilizing indoor set C ~ E to carry out cooling and warming, any one party of Intermediate Heat Exchanger 40a, 40b plays a role as evaporimeter and obtains cold water, and the opposing party plays a role as condenser and obtains hot water simultaneously.Now, according to refrigeration load and the ratio heating load, switch the connection of four-way switching valve 2, outdoor heat exchanger 3 carries out the selection of evaporimeter or radiator, carries out the running of refrigeration main body or heats main body running.The P-h line chart of kind of refrigeration cycle side is now identical with Fig. 7, identical with Fig. 8 in the case of injection when not injecting during main body of freezing operates, identical with Fig. 9, identical with Figure 10 in the case of injection when not injecting in heating main body and operating.The work of kind of refrigeration cycle side and embodiment 1,3 almost identical.
Above, in conditioner 500, pump 41a, 41b, indoor heat exchanger 5c ~ 5e and Intermediate Heat Exchanger 40a, 40b are connected and form the closed circuit that second refrigerant is circulated, and indoor heat exchanger 5c ~ 5e carries out heat exchange to second refrigerant and indoor air.Accordingly, according to conditioner 500, even if cold-producing medium leaks from pipe arrangement, cold-producing medium also can be suppressed to invade air-conditioning object space, safer structure can be made.
In addition, as above-mentioned embodiment 1 ~ 3, when utilizing cold-producing medium to carry out carrying from repeater B to the heat of indoor set C ~ E, first flow control device 9c ~ 9e is arranged near indoor heat exchanger 5c ~ 5e.On the other hand, according to embodiment 4, when carrying out heat conveying with refrigerating medium, even if because of as the pressure loss in first indoor pusher side refrigerant piping 6c ~ 6e, the second indoor pusher side refrigerant piping 7c ~ 7e of refrigerating medium pipe arrangement, also can not there is the variations in temperature of refrigerating medium, volume control device 43c ~ 43e can be set in repeater B.And, if arrange volume control device 43c ~ 43e in repeater B, the temperature difference come and gone of carrying out refrigerating medium controls, then air-conditioning object space indoor such as the control valve of volume control device 43c ~ 43e etc. away from, thus can reduce the driving of control valve, valve by time the noise propagated to indoor set of the flow noise etc. of cold-producing medium.
In addition, due to repeater B can be utilized to carry out flow-control in the lump, so the control in indoor set C ~ E utilizes the situation of indoor remote controller, temperature sensor to close or whether off-premises station carries out the control that the information of defrosting etc. only carries out fan.And the heat utilizing cold-producing medium to carry out machine A to repeater B is outdoor carried, accordingly, the pump that the driving of refrigerating medium can be made to use is miniaturized, reduces the transmitting power of refrigerating medium further and realizes energy-conservation.In addition, can reduce the discharge temperature of compressor 1, compressor 1 can operate with the state that reliability is high.In addition, here, the loop structure of off-premises station A for benchmark, but also can adopt the loop structure of conditioner 100,200 or 400 with conditioner 300.
Above, according to the conditioner 500 of embodiment 4, in the same manner as the conditioner 100 of embodiment 1, when arbitrary operation mode, discharge temperature can both be reduced, compressor 1, with while the state running that reliability is high, can realize the running of the excellent in efficiency corresponding to the load of indoor.
Embodiment 5
Figure 21 is the summary loop structure figure of an example of the refrigerant loop structure of the conditioner 600 representing embodiments of the present invention 5.Based on Figure 21, conditioner 600 is described.In addition, preferably in 5, by with the difference of above-mentioned embodiment 1 ~ 4 centered by be described, about the part that refrigerant loop structure etc. is identical with embodiment 1 ~ 4, omit the description.In addition, about each operation mode performed by conditioner 600 and the control under each operation mode, identical with the conditioner 100 of embodiment 1, thus omit the description.
In conditioner 600, it is different from the conditioner of embodiment 1 ~ 4 that connection off-premises station A and the pipe arrangement of repeater B become 3 this respects from 2.Arrange the 3rd refrigerant piping 34 in the mode of the first branch 10 of the discharge pipe arrangement and repeater B that connect the compressor 1 of off-premises station A, second refrigerant pipe arrangement 7 is connected the second branch 11.That is, in conditioner 600, be fed into by the 3rd refrigerant piping 34 this point of indoor set carrying out heating from the cold-producing medium of compressor 1 discharge different from the conditioner of embodiment 1 ~ 4.In addition, about the flowing of cold-producing medium, roughly the same with the flowing utilizing Fig. 3 ~ 10 to illustrate in embodiment 1, thus omit.
Above, according to the conditioner 600 of embodiment 5, in the same manner as the conditioner 100 of embodiment 1, when arbitrary operation mode, discharge temperature can both be reduced, compressor 1, with while the state running that reliability is high, can realize the running of the excellent in efficiency corresponding to the load of indoor.
In embodiment 1 ~ 5, be illustrated for the situation that indoor set is 3, but connect several all right.In addition, in embodiment 1 ~ 5, be illustrated for the situation comprising reservoir 4, but also reservoir 4 can not be set.
The explanation of Reference numeral
1 compressor, 2 four-way switching valves, 3 outdoor heat exchangers, 3-1 outdoor heat exchanger, 3-2 outdoor heat exchanger, 3-a volume control device (outdoor fan), 4 reservoirs, 5 indoor heat exchangers, 5c indoor heat exchanger, 5d indoor heat exchanger, 5e indoor heat exchanger, 5-m volume control device (indoor fan), 5c-m volume control device (indoor fan), 5d-m volume control device (indoor fan), 5e-m volume control device (indoor fan), 6 first refrigerant pipings, the indoor pusher side refrigerant piping of 6c first, the indoor pusher side refrigerant piping of 6d first, the indoor pusher side refrigerant piping of 6e first, 7 second refrigerant pipe arrangements, the indoor pusher side refrigerant piping of 7c second, the indoor pusher side refrigerant piping of 7d second, the indoor pusher side refrigerant piping of 7e second, 8a magnetic valve, 8b magnetic valve, 8c magnetic valve, 8d magnetic valve, 8e magnetic valve, 8f magnetic valve, 8g magnetic valve, 8h magnetic valve, 8i magnetic valve, 8j magnetic valve, 9 first flow control device, 9c first flow control device, 9d first flow control device, 9e first flow control device, 10 first branches, 11 second branches, 12 gas-liquid separation devices, 13 second amount control devices, 14a first bypass pipe arrangement, 14b second bypass pipe arrangement, 14c bypass pipe arrangement, 15 the 3rd volume control devices, 16 second heat exchangers, 17 First Heat Exchangers, 18 check-valves, 18-1 check-valves, 18-2 check-valves, 19 check-valves, 20 check-valves, 21 check-valves, 21-1 check-valves, 21-2 check-valves, 22 the 4th volume control devices (outside volume control device), 23 injection pipe arrangements, 24 the 5th volume control devices (injected current amount control device), 24-1 volume control device, 24-2 open and close valve, 25 the 3rd bypass pipe arrangements, 26 the 6th volume control devices (bypass flow control device), 26-1 volume control device, 26-2 open and close valve, 27-1 open and close valve, 27-2 open and close valve, 27-3 open and close valve, 28 check-valves, 29 check-valves, 30 check-valves, 31 check-valves, 32 gas-liquid separation devices, 33 the 3rd heat exchangers, 34 the 3rd refrigerant pipings, 40a Intermediate Heat Exchanger, 40b Intermediate Heat Exchanger, 41a pump, 41b pump, 42c magnetic valve, 42d magnetic valve, 42e magnetic valve, 42f magnetic valve, 42g magnetic valve, 42h magnetic valve, 42i magnetic valve, 42j magnetic valve, 42k magnetic valve, 42l magnetic valve, 42m magnetic valve, 42n magnetic valve, 43c volume control device, 43d volume control device, 43e volume control device, 50 control device, 50a memory, 51 pressure gauges, 52 pressure gauges, 53 pressure gauges, 54 thermometers, 60a first connecting pipings, 60b second connecting pipings, 60c pipe arrangement, 100 conditioners, 200 conditioners, 300 conditioners, 400 conditioners, 500 conditioners, 600 conditioners, A off-premises station, B repeater, C indoor set, D indoor set, E indoor set.

Claims (9)

1. a conditioner, is characterized in that, has:
Compressor, it can inject the cold-producing medium of pressure by injection pipe arrangement in the compression midway of cold-producing medium;
Outdoor heat exchanger;
Flow passage selector device, it switches the connection of described outdoor heat exchanger;
Injected current amount control device, it controls the injection flow to described compressor;
Outside volume control device, it can generate presses in injecting to described compressor, and flow path resistance is changed continuously;
Bypass flow control device, it can be arranged on described outside volume control device the bypass pipe arrangement making described outdoor heat exchanger bypass in parallel, and the heat exchange amount of described outdoor heat exchanger is controlled together with the volume control device of described outside, flow path resistance is changed continuously;
Indoor heat exchanger; With
Indoor volume control device, it adjusts the refrigerant flow to described indoor heat exchanger,
Described compressor, described outdoor heat exchanger, described flow passage selector device, described injected current amount control device, described outside volume control device, described bypass flow control device are built in off-premises station,
Described indoor heat exchanger, described indoor volume control device are built in indoor set,
Described indoor set is connected multiple with described off-premises station in parallel,
The end side of described injection pipe arrangement is connected to described compressor, and another side is connected to the refrigerant flow path be connected with described outside volume control device,
The end side of described bypass pipe arrangement is connected between described flow passage selector device and described outdoor heat exchanger, between another side that another side is connected to described outside volume control device and described injection pipe arrangement and the coupling part of described refrigerant flow path,
Following control is switched according to indoor load or outer temperature degree:
The control of the heat exchange amount of the described outdoor heat exchanger of described outside volume control device and described bypass flow control device; With
The control of the Stress control of the described middle pressure of described outside volume control device, described bypass flow control device and described injected current amount control device and the injection flow to described compressor,
When carrying out the control of described injection flow, do not carry out the control of the heat exchange amount of described outdoor heat exchanger, described bypass flow control device cuts out.
2. conditioner as claimed in claim 1, it is characterized in that also having repeater, described repeater is between described off-premises station and described indoor set, and switch refrigerant flow path and cooling and warming mixing running can be realized, so that described indoor set carries out freezing or heating respectively.
3. conditioner as claimed in claim 1, it is characterized in that, described outside volume control device and described bypass flow control device are according to described outer temperature degree, switch the control of the heat exchange amount of described outdoor heat exchanger, and the control of the Stress control of described middle pressure and the injection flow to described compressor.
4. conditioner as claimed in claim 1, it is characterized in that, according to outer temperature degree, at least one service data in the frequency of the pressure in the operating number of the cooling and warming of indoor temperature, described indoor set, described conditioner, temperature, described compressor, switches the control of the control of the heat exchange amount of described outdoor heat exchanger and the injection flow to described compressor.
5. conditioner as claimed in claim 1 or 2, it is characterized in that, no matter described outdoor heat exchanger carries out the situation of work as condenser or carries out the situation of work as evaporimeter, and the flow direction of the cold-producing medium flowed in described outdoor heat exchanger all becomes constant direction.
6. conditioner as claimed in claim 1 or 2, is characterized in that,
The Structure composing that described outside volume control device and described bypass flow control device can be changed continuously by flow path resistance,
Described heat exchange amount controls to be changed continuously by the flow of the cold-producing medium making the described outdoor heat exchanger of inflow to carry out.
7. conditioner as claimed in claim 1 or 2, is characterized in that, as the cold-producing medium of thermal source, employs difluoromethane or comprises difluoromethane and tetrafluoropropane and the quality ratio of difluoromethane is the mix refrigerant of more than 15%.
8. conditioner as claimed in claim 1 or 2, it is characterized in that, the discharge temperature that the control to the injection flow of described compressor is controlled so as to the cold-producing medium of discharging from described compressor is no more than 110 DEG C.
9. conditioner as claimed in claim 2, is characterized in that,
At described outdoor heat exchanger as in the operation mode of evaporator operation,
When the situation and at least one indoor set of not carrying out the indoor set freezed are freezed, the desired value of middle pressure is different.
CN201280067172.XA 2012-01-23 2012-01-23 Conditioner Active CN104053959B (en)

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